Hydraulic duplicating mechanism and directional control



NOV. 27, 1945. TURCHAN ETAL 2,389,653

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 26, 1943 7 Sheets-Sheet 1 INVENTORS N/J/YUEL THEE/#70 BY z'u/Pr/s WALKER Nov. 27, 1945. M. TURCHAN ETAL 2,389,553

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 26, 1945 7 Sheets-Sheet 2 /38 INVENTORS 40 Nfl/VJEL TUMf/fl/Y Cl/PT/S W/YLKER @M 42% Nov. 27, 1945. 'M, TURCHAN ETAL 2,389,653

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 26, 1943 I 7 She'ets-Sheet 3 ATM/W75)? 1945. M. TURCHAN ETAL 2,389,653

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 26, 194:: '7 Sheets-Sheet 4 Nov. 27, 1945. M. TURCHAN ETAL 2,339,653

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 2s, 194s ,7 Sheets-Sheet 5 fig/l7. MENTOR;

"F MXZW'W Nov. 27, 1945. M7 TURCHAN ETAL 2,389,653

HYDRAULIC DUPLICATING MECHANISM AND DIRECTIONAL CONTROL Filed July 26, 1943 7 Sheets-Sheet 6 gatented Nov. 27, 1945 HYDRAULIC DUPLICATHVG MECHANISM AND DIRECTIONAL CONTROL Manuel Turchan, Deal-born, and Curtis Walker, Detroit, Mich.

Application July 26, 1943, Serial No. 496,240

41 Claims. (o1. 90--13.5)

This invention relates to a machine tool duplieating attachment, and more particularly to an automatically controlled mechanism governing relative circumambulatory movement of a cutter and a work table supported work-piece.

Still more particularly the invention relates to means governing relative longitudinal and cross feeding movement of a cutter and a work-piece whereby a pattern or templet of irregular shape may be completely reproduced by a continuous relative 360 degree traverse of the cutter with respect to the work-piece; or by a plurality of continuous 360 degree traverses.

It will be understood that the templet and work-piece are supported in spaced relation upon a suitable work table, as for instance the work table of the machine tool to which the present attachment is adapted to be secured, with a tracer provisioned relative to said templet and adapted for circumambulatory 360 degree movement with respect thereto.

Movements of the tracer spindle reacting to the sides of the templet are adapted to control alternately the longitudinal and cross feed of said work table and cutter, there being hydraulic motors or cylinders secured to said table at right angles, with their hydraulic fluid pressure connections from a suitable hydraulic unit being governed by said tracer.

In the present invention however, only one feed cylinder, either longitudinal or cross feed, will at any moment be under tracer control. While one cylinderis thus under tracer control the other is under constant fluid control from the hydraulic unit, through a directional control valve, and entirely independent of the tracer.

It being desirable at diflerent points in a circumambulatory traverse around a work piece and templet pattern to change tracer control from one feed to the other, a suitable directional con trol valve is employed the detail of which is set out below and in our co-pending application Serial Number 449,354, filed July 1, 1942.

However said directional control valve receives one of two sources of tracer controlled fluid to be directed to one end or the other of either of the two feed cylinders. Said directional control valve also receives a constant fluid source from a hydraulic unit to be directed to one end or the other of the feed cylinder not under tracer control. By quarter turns of the directional control valve in one direction or the other, as explained hereafter in detail, there can be a complete relative circumambulatory traverse of 360 degrees, or a plurality of such traverses of the work-piece relative to the cutter, at the same time as similar relative movements are effected between the templet and tracer.

It is the object of the present invention to provide an automatic tracer operated control for the directional control valve whereby rotary adjustments of said valve may be made automatically so that no matter what the shape is of the pattern sought to be reproduced, a complete 360 degree traverse of its surfaces may be made without manual adjustment of the directional control valve.

It is a further object of the present invention to provide a hydraulically actuated piston operably connected to the directional control valve for efl'ecting quarter turns successively in one direction, together with another hydraulically actuated piston operably connected to-said directional control valve for effecting quarter turns successively thereof in the opposite direction.

It is the further object hereof to provide a tracer controlled valve for directing fluid impulses to one of said pistons or the other to thereby automatically control the rotary quadrantal adjustment of said directional control valve.

It is the still further object herein to provide a constant fluid source from the hydraulic unit to said pistons for returning the same respectively to their inoperative positions after having eiiected a quarter turn of the directional control valve, whereby upon the next fluid impulse, the pistons will be ready, one or the other to effect an additional quarter turn of the directional control valve in one direction or the other.

It is the still further object of this invention to provide a tracer having a spindle controlled valve adapted for directing fluidfrom the hydraulic unit to one end or the other of either the longitudinal or cross feed cylinder depending upon longitudinal positions of said valve above or below a certain predetermined neutral position.

It is the further object herein to provision exhaust fluid governing means within said spindle actuated valve whereby exhaust fluid from both feed cylinders can be directed therethrough before being returned to the hydraulic unit, it being understood that such control of the exhaust fluids from the feed cylinders also effects control of the feeding of the work table, slowing down the same in proportion to the amount of spindle deflection.

. Thus while a reasonably small deflection may result in partial slowing down of the feed movement, an extreme or abnormal deflection may cause actual stoppage of both feeds, preventing damage to the work piece, to the cutter or to the tracer under certain conditions.

It is the further object of this invention to provide an automatic control for the directional control valve characterized by a plurality of piston operated lever mechanisms for eifecting one quarter rotational adjustments of said directional control valve.

It is the further object herein that said lever mechanisms be actuated electrically under the control of the tracer mechanism, as by a plurality of solenoids, for accomplishing the desired translational movement 01' said lever mechanisms.

It is the further object herein to provide a third dimensional vertical control in combination with the two directional horizontal control, with a suitable secondary tracer adaptable for engagement with a model, thereby providing a completely automatic three directional controlled duplicating attachment.

These and other objects will be seen in the following specification and claims showing the various elements and their various operative combinations, as illustrated in the accompanying drawings of which- Fig. 1 is a front elevational view of a milling machine showing the duplicating'attachment.

Fig. 2 is a partially sectional complete diagrammatic view illustrating the hydraulic connections and operative relations of the control mechanisms.

Fig. 3 is a diagrammatic view of a regularly shaped pattern with the numbered arrows indicating positions of the tracer spindle and the corresponding adjusted positions of the directional control valve rotary member.

Fig. 4 is a diagrammatic view of an irregularly shaped pattern with the numbered arrows indicating progressive positions of the tracer spindle and directional control valve rotary member.

Fig. 5 is a diagram indicating the four radial positions of the directional control valve rotary member.

Fig. 6 is an elevational section of one form of directional control valve actuating mechanism.

Fig. 7 is a section on line 1-1 of Fig. 6.

Fig. 8 is a partially sectioned enlarged diarammatic view of a directional control valve automatic control. i

Fig. 9 is a partial section on line 99 of Fig. 6.

Fig. 10 is a wiring diagram for a tracer controlled electrically operative mechanism for rotatably actuating the directional control valve rotary member.

Fig. 11 is a partially sectioned view of the directional control valve rotary member 11.

Fig. 12 is a section on line l2-l2 of Fig. 11.

Fig. 13 is a section on line l3-l3 of Fig. 11.

Fig. 14 is a section on line l4-l4 of Fig. 11.

Fig. 15 is a section on line 15-5 of Fig. 11.,

Fig. 16 is a section on line l6 l6 of Fig. 11.

Fig. 17 is an elevational view of a difierent form of directional control valve actuating mechanism.

Fig. 18 is a top plan view thereof.

Fig. 19 is an end view thereof.

Fig. 20 is a fragmentary partially sectioned view showing a slightly different arrangement of the two directional control tracer and the automatic control mechanism for the directional control valve coupled thereto.

The above drawings illustrate merely preferable embodiments of the invention herein, it being distinctly understood that other embodiments are contemplated within the scope of the invention hereinafter set out, described and claimed.

Referring to the drawings, Fig. 1 shows a standard milling machine with supporting base ll, longitudinally adjustable work table II, and the transversely adjustable cross feed work table supporting slide [3.

Slide I3 is suitably supported upon base ll, there being a cross feed cylinder l4 secured to said slide adapted for reciprocable movement with respect to a stationary piston l4 and piston rod l4" therein anchored to said base. Similarly work piece and templet supporting table I! is longitudinally reciprocable by means of the reci procable cylinder l5 secured thereto and adapted for movement with respect to the stationary piston I6 and piston rod H, the latter being suitably anchored to the cross feed slide 13 A cutter I8 is rotatably journaled above table l2 with provision made for vertical adjustment as desired by means of the vertically adjustable slide l9 which suitably supports cutter [8, said slide itself being adjustably provisioned upon the upright portion 20 forming a part of the base H of the milling machine.

A movable cylinder 2 is suitably secured to slide l9 adapted for reciprocable vertical movement with respect to the stationary piston 3 and piston rod 4 secured to the column 20 at point 5.

Tracer 2| is carried by column I I being universally mounted for adjustment relative to cutter l8, there being a supporting arm 22 secured to column I I, to which is secured vertical tracer adjustment means 23, longitudinal adjustment means 24 and the cross adjustment means 25.

The secondary tracer 6 governing vertical feed movements of cylinder 2 is carried by the bracket I joined to the vertically adjustable slide l9 and movable therewith, there being a vertically ad- ,J'ustable means 8 interposed therebetween for positioning said tracer relative to model 9 on work table l2.

Spindle 28 having a pattern engaging tracer tip 21 is longitudinally disposed within tracer housing 2| as shown in Fig. 2, carrying at its upper end the cylinder control valve piston 28'. Said piston having annular openings 29, 30, 3|, 32 and 33 is adapted for slight reciprocable movement within tracer sleeve. II) which has corresponding annular fluid conducting openings 34, 35 and 39.

A piston rod 31 is carried at the upper end of piston 28 being slidably disposed through nut 33 and the spring tension adjusting nut 39 for'the valve piston engaging spring 40. A bracket member 4| disposed across the top of tracer sleeve 10 and suitably secured thereto carries at its other end the control housing 42 which has provisioned therein the annular openings 43 and 44.

A control piston 45 having fluid conducting annular openings 46, 41 and 48 is slidably disposed within housing 42, and adapted for longitudinal adjustment therein by means of'the upwardly extending piston rod 49 suitably secured thereto. Piston rod 49 is actuated reciprocably by lever 50 pivoted at 5| to thefulcrum 52,- its respective ends carrying studs 53 and 54 which are respectively nested within the discs or members 55 and 56 carried by piston rods 49 and 31.

Thus upon movement of spindle 26 upwardly on engaging an irregularity or change in the contour of the templet movement may be also imparted downwardly to the control piston 45. It will be understood however that it is desirable that the relative movement of piston 28 and piston 45 be unequal; and this can be accomplished by regulating the operative ends of lever 50.

On the other hand downward movement of spindle 26 under action of spring 40 will cause an upward movement of the control piston 45. It will be understood that such downward movement of spindle 26 may represent a substantial change in direction of the peripheral surface of the templet.

Referring to Fig. 2 the hydraulic unit is generally indicated at 51 for supplying fluid under pressure by means of a suitable pump, not shown, out through conduit 58 to the tracer sleeve opening 30, through conduit 59 to the control housing opening 41, through conduit 60 to port 60' of the directional control valve housing GI, and through conduit 62 to the ends of the directional control valve operating cylinders 63 and 64.

In neutral position of valve piston 28 with the tracer tip 21 out of engagement with the templet, it will be noted that by action of the 1 spring "I said piston will be slightly below the position shown in Fig. 2. Fluid directed from the hydraulic unit 51 through conduit 58 and sleeve opening will then enter valve opening 34 and be directed out through conduit 61 to the directional control valve 6| at port 61'.

In the manner fully set out hereunder said fluid is directed, in one position of the directional control valve rotor member 11 to one end for instance, of longitudinal feed cylinder l5 through conduit 66 causing tracer controlled longitudinal feeding of work table IE to the right.

With tracer controlled fluid directed through conduit 66, exhaust fluid returns to the directional control valve through-conduit 68, and to the tracer through conduit 65 to enter valve opening 35. It will be noted that in the previously depressed position of piston 28 said exhaust would be free to enter sleeve opening 3| for direction through conduit 69, governor inlet 32, opening 36, and governor outlet 33, to be returned to the hydraulic unit 51 through conduit 10.

As soon, however, as the tracer tip 21 contacts the pattern slightly, spindle 26 will be projected upwardly to its central inoperative position so that further longitudinal feeding is stopped, inasmuch as fluid from opening 30 can no longer enter valve opening 35. As cross feeding at the moment, hereafter described in detail is constant, in accordance with a change in the contour of the templet 21', spindle 21 will be projected upwardly so that fluid at opening 30 will be conducted into valve opening and thence through conduit 65 to the directional control valve at port 65.

With the directional control valve in its same adjusted position, said tracer controlled fluid is then conducted to the opposite end of the longitudinal feed cylinder 15 through conduit 68 causing an immediate reversal of longitudinal feeding to the left.

In this same position of the rotary member 11 of the directional control valve exhaust fluid from cylinder i5 is conducted back to the direction control valve through conduit 66, whence said exhaust is directed back to the tracer through onduit 61, where in the elevated position of pison 28, it is free to enter the exhaust opening 29. Said exhaust fluid is then directed to exhaust conduit 69 into the exhaust governor inlet 32 where it communicates with sleeve opening 36, valve opening 33, and conduit 10 back to the hydraulic unit 51.

As set out in detail in the above referred to co-pending application, Serial No. 449,354 relating to the directional control valve, and also in our co-pending application, Serial No. 366,082, relating to two directional feed control, with tracer controlled fluid directed to the longitudinal feed cylinder l5 through conduits 66 or 68, the cross feed cylinder I4 is under constant feeding. Fluid under pressure is supplied from the hydraulic unit 51 directly to the directional control valve through conduit 60 where in the same position of the rotary member therein constant fluid will be directed to one end of the cross feed cylinder l4, for instance through conduit 1|. With the piston stationary, cylinder l4 moves outwardly towards the observer, while the exhaust fluid on the other side of the piston is returned through conduit 12 back to the directional control valve.

From the directional control valve the exhaust fluid returns through conduit 13 to the tracer controlled exhaust governor inlet 32, passing through the sleeve opening 36, and governor outlet 33, back to the hydraulic unit 51 through con- It will be understood that constant fluid under pressure, independent of the tracer, may be directed from the directional control valve through conduit 12 which would cause constant cross feeding outwardly in the opposite direction, away from the observer. In this event the exhaust fluid returns through conduit 1| to the directional control valve, and then through conduit 13 to governor openings 32, 36, 33, and conduit 10 back to the hydraulic unit.

In reproducing a work-piece from a templet where a 360 degree circumambulatory traverse is contemplated, or a plurality of such traverses accompanied by an indexed relative vertical feedin is intended, or an automatictracer controlled vertical feeding, it is desirable that the tracer tip pressure against the edge of the templet be substantially tangent to the surface thereof at its point of contact. Asshown in Fig. 3 for instance by the numbered arrows I, 2, 3 and 4 arrangedmround the diagrammatic indication of the regularly shaped pattern 14, the co-action of the tracer tip shown by said arrows is perpendicular to the point of contact of the tracer and also towards the templet.

As set out in our co-pending applications Serial No. 449,354 and Serial No. 366,082, the number l arrow indication represents the position of the rotary member 11 of the directional control valve 6| which will provide tracer control to the cross feed cylinder at the time that the longitudinal feed cylinder is under constant feeding. With the tracer spindle relatively stationary and with the templet 21' upon the work table l2 being fed relative thereto it is desirable that in effect, a circumambulatory traverse of the pattern be obtained, so that in efiect the tracer relatively walks completely around the templet.

As the tracer relatively nears one end of the pattern in order to maintain the tracer tip 21 action towards and substantially perpendicular to the pattern or templet it is necessary to effect a quarter turn of the direction control valve rotor 11 in for instance, a clockwise direction, which has the effect of changing tracer control to the.

longitudinal feed cylinder and changing constant feeding to the cross feed cylinder. This position of the directional control valve is indicated b the arrow indication number 2.

The number 3 arrow indication with tracer control again in a cross feed cylinder is obtained tional control valve.

Fig. diagrammaticalb indicates the four quadrantal positions oi. the rotary member of the directional control valves numbers I, 2, a and l, in order to obtain the inward urge of the tracer tip towards and substantially perpendicular to the edge of the templet throughout the relative circumambulatory traverse of the tracer with respect thereto.

It will be seen that when the edge of the templet is substantially regular as shown in Fig. 3, the progressive one quarter turns of the directional control valve are all in the same clockwise direction for obtaining a complete 360 degree circumambulatory traverse of the templet.

Naturally the tracer movement can be reversed in direction, or at least the relative movement by progressive quarter turns of the directional control valve rotor I1 in the opposite or counterclockwise direction.

From the numbered arrow indications shown in.the irregularly shaped templet 15 in Fig. corresponding to the required positioning shown in Fig. 5, for obtaining an inward substantially right angular urge of the tracer tip relative to the templet it is seen that the quarter turns required will not all be in the same direction but will be varying as indicated.

Thus after the first three one quarter turns of the directional control valve in a clockwise direction, referring to Fig. 4, it will be necessary a to go from the number 3 position back in a counterclockwise direction one quarter of a turn to again go to the number 2 position. Again the next adjustment of the directional control valve will be another one quarter turn in a counterclockwise direction to obtain the number I position again.

Progressively the next adjustment will again be clockwise one quarter turns to positions I, 2, 3 and' 4, then counterclockwise progressively one quarter turns to the number 3 and number 2 positions etc.

Thus it is seen that for an irregular circumambulatory traverse, the directional control valve will not be operated entirely clockwise in quarter turns, but will be intermittently turned clockwise and then colmterclockwise, a quarter turn at a time until a complete traverse is obtained.

The hand wheel I6 shown in Figs. 1 and 2 is adapted to accomplish manually the necessary quarter turns of the directional control valve as desired in the manner previously above set out in detail. However as hereafter described, means are provided for obtaining suchdirectional control valve adjustment automatically without the attention of an operator, and entirely independent of the above referred to hand wheel 16.

Referring to Fig. 2 and also Figs. 11 through 16 the directional control valve is indicated at 6| with the four cylinder ports 66', 66'; I2 and II. Constant pressure fluid from hydraulic unit 51 is directed to the directional control valve at port 60' through conduit 66, to be exhausted through port 13' and conduit 13 back to the tracer as above described.

The directional control valve housing 6| has a tracer controlled fluid source coming in through conduit 66 at port 65' and returning to the tracer fluid entering at port 60' out through any of the cylinder ports 66', 66', I2 or II. Likewise said rotatable member is adapted to direct tracer controlled fluid coming into the directional control valve at either port 65' or 61' out through one of the cylinder ports II, or 12, 66' or 66.

Furthermore said rotor 11 provides exhaust connection for the other two cylinder ports not delivering fluid, either constant pressure or tracer controlled. Constant pressure exhaust fluid is conducted back to the directional control valve exhaust port 13 to be directed back to the tracer governor through conduit I3 as above described in detail.

Further, exhaust fluid from the cylinder under tracer control is returned through said rotatable member to either port 61' or 65' back to the tracer through either conduit 61 or 65 in the manner above described.

Said rotor, shown in Figs. ll-l6, has provisioned longitudinally therein the non-communicating passages I60, I6I, I62 and I63 all terminating at one end of said rotor in the four radially positioned passages I60, I6I, I62 and I63, each of which is adapted for progressive communication, on rotation of member IT a quarter turn at a time, with each of the ports 65', 60', I3 and 61' respectively shown in Fig. 2. It is understood that said quarter turn adjustments of rotor 11 are accomplished either manually through rotatable hand wheel I6 or automatically by the tracer operated automatic control fully described in detail hereinafter.

A plurality of annular recesses I64, I65, I66, I61 are provisioned within plunger 11 to coincide with the corresponding cylinder ports 66', 66', I2 and 'II' as shown in Fig. 2.

Longitudinal opening I60 terminates at outlet I68 within annular opening I64 to establish fluid communication with the corresponding cylinder port 66'. Longitudinal openings I6I, I62 and I63 all of varying lengths from opening I66 likewise respectively terminate at outlets I69, I16 and I'll provisioned around rotor 11, to establish fluid communication eil'ectively with the corresponding cylinder ports 66, 12' and II in the directional control valve housing 6|.

Consequently in turning the rotor 11 a quarter of a turn at a time i. e. ninety degrees in one direction or the other it is possible to establish communication from any one of the ports 66', 60, I3 and 61' in the direction control valve housing to any desired cylinder port 66', 66, 12' or II in said housing for providing fluid control to any particular end of either the longitudinal or cross-feed cylinders I 6 or I4. And at the same time to also provide communication from the other inlet ports 65, 66', II or 61' to each of the other remaining ends of said cylinders.

For example fluid under' constant pressure through conduit 60 from hydraulic unit 51 travels via port 60', passage I6I', channel I6I, outlet I69, cylinder port 66', and conduit 66 to one end of the longitudinal feed cylinder I5. Exhaust from the other end of said cylinder returns via conduit 66, cylinder 66, passage I68, ,channel I60, radial passage I60 and port 13' for direction through conduit 13 back to the tracer governor for subsequent exhausting.

At the same time tracer controlled fluid goes from conduit 65 into the directional control valve housing at port 65' and via passages I63, I63, outlet HI and port H, and conduit H to one end of the cross-feed cylinder I4. The exhaust from the other side thereof goes back via conduit 12, cylinder port 12' and passages I10, I62, I62, port 61' and conduit 61 back to the tracer.

In operation in progressively traversing the cutter I8 relatively around work-piece 6 corresponding to a relative circumambulatory traverse between the tracer 21 and the templet 21' if it is desired to change the constant feed from the longitudinal feed cylinder I to the cross-feed cylinder I4, with tracer control changed from the cross feed cylinder to the longitudinal feed cylinder, all that is necessary is to rotate the plunger 11 a quarter of a turn counterclockwise.

Constant feed travels via port 80', channels I63, I63, HI and port H and conduit H to one end of the cross feed cylinder I4. While exhaust from the other side of said cylinder flows back to th directional control valve via conduit 12, port 12', and channels I10, I62, I62, and port 13 and through conduit 13 back to the tracer.

At the same time tracer control goes to the longitudinal feed cylinder I5, via port 65' and channels I60, I60, I68, cylinder port 66 and conduit 66, to cylinder I5 and the exhaust on the other side of said cylinder returns via conduit 68, port 68 and channels I69, I6I, I6I', and port 61' and conduit 61 back to the tracer for exhausting through the governor mechanism above described.

Thus it is seen that a versatile directional control valve is provided for governing longitudinal and cross feeding of the work piece supporting table with respect to a rotatable cutter whereby it is seen that upon adjustment of the directional control valve rotor in quarter turns at a time in one direction or the other that a complete 360 degree relative eircumambulatory traverse may be obtained between the cutter I8 and the work-piece I8 corresponding to a similar 360 degree relative circumambulatory traverse of the tracer 21 'with respect to the templet 21'.

Constant feeding may be changed from longitudinal feeding in one direction to cross feeding in one direction. By further rotation 90 degrees of rotor 11 constant feed may be again directed to the longitudinal feed cylinder in the opposite direction; and by another quarter turn of the hand wheel constant feed could go to the cross feed cylinder in the opposite direction.

Referring to Figs. 2 and 8 the shaft of the directional control valve rotary member indicated at 11 is adapted for rotation progressively in quarter turns either clockwise or counterclockwise. Generally the hydraulic control cylinders 63 and 64 are adapted for causing rotation of shaft 11. Cylinder 63 has therein a piston 18 and a reciprocable rod 19 the outer end ,of which is secured by bracket 80 to rack gear 8|.

Likewise cylinder 64 has reciprocably provisioned therein piston 82 and rod 83, on the outer end of which is secured the bracket 84 for transmitting longitudinal movement to the rack gear 86.

In Fig. 2 piston 82 is in its inoperative position being so adjusted by virtue of the constant fluid source directed to cylinders 63 and 64 through conduit 62 from the hydraulic unit 51.

As described hereafter there are two idler gears 86 and 81 on shaft 11 one adapted for rotating said shaft clockwise a quarter of a turn at a time and the other for rotating the shaft counter-clockwise one quarter of a turn at a time. These gears each respectively turn the shaft in only one direction, and movement of the gears respectively in the opposite direction is merely an idling motion permitting each of the rack gears to return to its initial inoperative position ready for the hydraulic impulse from the control valve hereafter described which will cause its longitudinal gear operating movement. I

Fluid under pressure from hydraulic unit 51 is supplied through conduit 59 to the control housing opening 41 where, depending upon movement of control piston 45, is adapted to be directed outwardly through either piston opening 43 or 44 to conduits 88 or 88 respectively. Conduit 88 directs fluid to the end of control cylinder 63 and conduit 89 directs fluid under pressure from the control housing 42 to control cylinder 64.

Piston 18 of cylinder 63 is shown in Fig. 2 in its operative position at the end of its operative stroke after having translated rack gear 8I which is adapted to operatively engage the idler gear, for instance, gear 86, in the manner now described in detail in connection with Figs. 6 and 7.

The directional control valve fragmentarily indicated at 6| in Fig. 6 with its rotatable shaft member 11, is suitably secured to hand wheel 16 by the nut 90 and member I02, whereby said directional control valve may be manually adjusted to any of the various quadrantal positions previously described.

A cylinder supporting plate 8| is provided secured by studs 92 to the directional control valve housing 6|. plate 9|, being secured thereto by screws 93; while control cylinder 64 is secured thereto by screws 83.

Piston 18 is shown within cylinder 63 secured to the reciprocable rod 18 on the end of which is bolted bracket for reciprocating rack gear 8|, the latter being adapted for sliding reciprocable movement within the recessed longitudinal groove 94 formed within cylinder 63.

The corresponding rotatable idler gear 86 is provisioned in mesh with rack gear 8I being rotatably and loosely journaled on the rotatable sleeve 96, the latter being adapted for rotation with the rotatable member 11 forming the rotor for the directional control valve 6|.

It will be noted however that said rotatable sleeve is loose upon rotatable shaft 11 but may be locked with respect thereto for movement in unison therewith.

To accomplish this, sleeve 96 is slotted at 81 for receiving the reciprocable piston member 98 having an operating piston rod one end of which 89 projects through the outside of sleeve 86, while its other end I 00 is adapted to project within the transverse slot IOI formed within the rotatable member I02 secured to hand wheel 16 and also to rotatable member 11.

A manually operable cantilever handle I03 pivotally mounted at I04 is loosely secured at its operating end at I06 to the outer end 89 of Control cylinder 63 is carried by w piston rod I00. By action of coiled spring I06 piston 98 is normally urged inwardly causing the inner end I of the piston rod to be nested within opening I 0| of member I02.

So positioned, it is seen that rotary movement of sleeve 86 willcause movement in uni son therewith of hand wheel 16 and likewise rotary movement of the directional control valve rotary shaft 11, when under automatic operation. However, on manual operation of handle I03 in a clockwise direction, sleeve 96 is disengaged, and hand wheel 16 may be manually operated independently of sleeve 96 and the automatic control.

Thus it is seen that during automatic operation, now described further, hand wheel 16 is adapted to also move corresponding to the rotary movement of sleeve 96.

Rotary member I02 secured to the rotatable shaft 11, is radially slotted at I06 for slidably nesting ratchet member I01, the latter being itself recessed for receiving coiled spring I08 which is adapted to normally urge said ratchet member outwardly with respect to member I02 and within a corresponding notch I09 shown in Fig. 7, formed within the inner surface of the idler gear 86. It wil be noted that ratchet I01 projects up through a suitable opening 95 in sleeve 96.

Said ratchet member is angularly inclined at I I0 whereby it is seen that movement of idler gear 86 independent of member I02 will be permitted in one direction only i. 'e. clockwise as it is returned by action of rack gear 8| to its initial position. 0n the other hand it will be noted upon rotation of idler gear 86 in a counterclockwise direction upon longitudinal translation of rack gear 8| to the left under action of the automatic control that said rotation of gear 86 will cause a corresponding quarter turn rotation counter-clockwise of the rotatable member I02 and the rotor 11 of the directional control valve 6 I.

Immediately after this initial fluid impulse from conduit 88 causing a quarter turn counterclockwise of the directional control valve rotary member, piston 18 will be promptly returned to its initial position to the ,right by virtue of the constant fluid pressure provided from the hydraulic unit through conduit 62. 1

Consequently it will be seen that piston member 18 i again ready for another fluid impulse from the hydraulic control valve causing longitudinal movement of rack gear 8| to the left and another quarter turn counter-clockwise movement of the rotor member 11. It is seen that after each progressive quarter turn idler gear 86 is returned clockwise to its initial position which is readily permitted forcing the ratchet member I01 inwardly against the action of coiled spring I08.

In a similar manner it will be seen that rotatabl member I02 is also radially slotted at I II for slidably receiving the ratchet member 2 which is also slotted for receiving the coiled spring 3 interposed therebetween and the rotatable member I02. It will be noted that ratchet member 2 as shown in Fig. 9 is provided with an angular surface 4 oppositely inclined from the angular surface 0 of ratchet member I01, whereby said ratchet is adapted for operative engagement with idler gear 81 which is loosely J'ournaled also around the rotatable sleeve 96, said gear also having a ratchet recess -II for receiving operatively the upper end of ratchet I I2.

Consequently it will be seen that longitudinal movement of piston 82 in cylinder 64 to the left causing a corresponding longitudinal movement of rack gear 82 thus causes a clockwise movement of idler gear 81 which by the position of ratchet member 2 i adapted to cause a clockwise movement of rotatable member I02 and the rotor 11 secured'thereto.

Similarly after the initial stroke of rack gear to the left, fluid under pressure from the hydraulic unit 51 through conduit 62 immediately returns piston 82 to its initial position, to the right at the same time returning rack gear 85 and idler gear 81 which is free to rotate in a counter-clockwise direction without effecting movement of the rotary member I02. Thus it is seen that idler gear 81 is again ready for its next hydraulic impulse from the hydraulic control housing 52 through conduit 89 whereby an-- other quarter movement in a clockwise direction of rotor 11 would be obtained.

As previously explained the control housing 42 provides fluid supply conduit; 88 and 89 respectively to the ends of the cylinders 63 and 64. Thus, depending upon the positioning of piston 4.5 within control housing 42, fluid will be directed through either conduit 88 or 89, or alternately through either conduit or by successive fluid impulses through either of said conduits. This will result in obtaining automatic movements of the directional control valve rotor member 11 continuously in a counter-clockwise direction as indicated by the successive numerals I, 2, 3 and 4 in Fig. 3, utilizing merely the control cylinder 64.

Or on the other hand in the case of an irregularly shaped pattern as shown in Fig. 4 the directional control valve rotor member will be actuated successively clockwise and then counter-clockwise depending upon the curvature of the pattern as shown in Fig. 4.

From the above description it is seen on longitudinal translation of rack gear 8| as in Fig. 7, causing counter-clockwise one quarter rotation of th idler gear 86 and consequent counterclockwise one quarter rotation of the directional control valve rotor 11, that immediately after this movement, by action of constant low pres- .sure fluid from the hydraulic unit 51 through conduit 62, rack gear 8| is returned to its initial position to the right ready for the next fluid impulse through conduit 88 from the tracer operated automatic hydraulic control valve.

The return of rack gear 8| to the right causes a clockwise free idler movement of gear 86 with the ratchet member I01 forced inwardly by action of the inner surface of said idler upon the inclined surface 0 of said ratchet.

In a similar manner translation to the left of rack gear 85 by action of fluid through conduit 89 causes clockwisemovement of idler gear 81 and likewise clockwise movement of the rotor 11 of directional control valve 6|. Similarly after its stroke to the left, fluid pressure is relieved in line 89 by piston 45 returning to a neutral position, and constant low pressure fluid through conduit 62 causes the rack gear 85 to return to its initial position at the right, with the ratchet member 2 forced inwardly by action of the inner surfac of said idler upon the inclined surface I of said ratchet. This in turn causes a. free counter-clockwise movement of idler gear 81 independent of rotatable members I02 and 11 returning said idler to its initial inoperative position.

Operation In operation, referring to Figs. 3 and 4, it is noted that templets 14 and 15 respectively have certain critical points of change in curvature direction, as for instance adjacent points H1, H8, H9 and I20 in Fig. 3. It is seen with the tracer tip 21 engaging templet 14, with constant longitudinal feeding to the left and tracer control in the cross feed, that when the tracer reaches the point II1, the change in direction becomes more sudden, permitting a more pronounced dropping away of the tracer tip 21, spindle 26 and also the tracer controlled valve 28.

This more pronounced downward movement is translated through piston rod 31, lever 50, piston rod 49, to the control piston 45 within control housing 42. Naturally this downward movement of tracer spindle 26 causes a corresponding upward movement of control piston 45 whereby fluid communication is intermittently established between the fluid line 59, port 41 and the control piston port 44. Thus fluid under pressure is directed out through conduit 89 causing piston 82 to traverse the length of its cylinder 84.

As above described this traverse causes a longitudinal operative translation of rack gear 85 causing rotation of idler gear 81 one quarter of a turn. In the manner above described a quarter or 90 degree rotation of the directional control valve rotor 11 is imparted, which has the effect of changing tracer control from the cross feed cylinder I4 to the longitudinal work table feed cylinder I5. At the same time, as above described, constant feeding is changed from the longitudinal feed cylinder I5 to the cross feed cylinder I4.

This reversal of tracer control again permits the tracer spindle 26 to assume a normal position, or at least is subject only to the normal amount of tracer deflection for normal tracer controlled feeding. Consequently, control piston 45 is returned to its initial neutral position cutting ofi the flow of fluid through conduit 89 to cylinder 64.

By action of the constant low pressure fluid from the hydraulic unit 51 through conduit 62, piston 82 is again returned to its normal inoperative position ready for the next fluid impulse from the control valve 45. I

Referring to Fig. 3 intermittent fluid impulses will be received progressively at approximately the marked points I I1, H8, I I9 and I20, each fluid impulse causing a quarter revolution of the directional control valve rotor 11. Said rotor therefore makes one complete 360 degree movement,

while the tracer and templet have also made a corresponding relative 360 degree traverse.

It will be noted here that the normal tracer deflection has no effect upon the control valve piston 45, this being accomplished by regulating the length of the arms of lever 50 so that the average normal deflection of the tracer spindle 26 will effect no fluid control through control valve housing 42.

It will be seen that for the traverse of the pat-. tern shown in Fig. 3, that only cylinder 64 need be employed for accomplishing the progressive clockwise quarter turns of the directional control valve rotor, inasmuch as tracer tip 21 on reaching each of the critical points H1, H8, H9 and I20 tends to drop to a greater extent than is otherwise encountered where the tracer covers the normal traverse, as for instance between points I20 and H1.

However referring to Fig. 4 it will be seen that the tracer tip if taken to be represented by the circled numerals, as it traverses relatively in a clockwise direction around the templet 15, will be adapted to relatively extreme downward movements as in Fig. 3, but also will encounter certain changes in direction which will cause a relatively extreme upward deflection as for instance at points HI and I22.

As the tracer tip reaches substantially the location of the point I'll an upward deflection occurs which will be greater than the normal upward deflection encountered as for instance the deflection encountered by the tracer when traversing templet 14, Fig. 3, from point I20 to point I23.

This upward deflection is similarly translated through piston rod 31, pivoted lever and piston rod 49, to cause a downward control movement of piston 45. This will result in establishing fluid communication from conduit 59 to port 41, and port 43, permitting fluid under pressure to be directed out through conduit 88 to the end of the control cylinder 63. Fluid so directed will cause a longitudinal translation of piston 18, and likewise of rack gear 8I causing a counter-clockwise quarter turn of the idler gear 86, which as previously explained causes a corresponding quarter tum of the rotor member 11 of the directional control valve 6 I. It will be noted that the quarter turn rotation caused by fluid traveling through conduit 88 is the opposite in direction from the quarter turn rotation caused by fluid traveling through conduit 89.

Consequently the directional control valve rotor 11 is changed from its number 3 position as indicated in Fig. 4 to its number 2 position. And again on the tracer encountering point I22 there will be another upward deflection which, in the manner above described, will cause another quarter rotation of the directional control valve rotor to its number I position.

As the tracer approaches the point I24 there will again be another pronounced downward movement of the tracer spindle 26 which will result in a quarter clockwise turn of the directional control valve rotor under action of fluid to cylinder 64..

It will be noted after the initial impulse of fluid from the control valve to either cylinder 63 or 64, that this supply of fluid is cut ofi with the result that low pressure fluid through conduit 62 causes return of the-pistons to their normal positions. From the illustration of Fig. 2 it will be seen that fluid in the upper part of cylinder 63, will be returned to the control valve housing through conduit 88, ports 43 and 46, whence it will be directed through conduit I25 back to the hydraulic unit 51. Similarly fluid returning through conduit 89 will be directed through piston recess 44, sleeve recess 48 and conduit I25 back to said hydraulic unit.

As above described in detail the directional control valve rotor 11 is adaptable to successive one quarter or ninety degree rotational adjustments in either a clockwise or counter-clockwise of the directional control valve in a clockwise direction.

n the other hand another switch is employed operable on accentuated upward movement of the tracer spindle. This latter switch is also adapted to cause the operation oi. another solenoid and lever for rotatably actuating the directional control valve rotor, one quarter of a turn at a time in the opposite or counterclockwise direction.

Referring to Fig. 10 a contactor I26 is shown adaptable to vertical upward or downward niovement being suitably mounted on the piston member 28 shown in Fig. 2.

On the other hand contactor I26 could be operable through the auxiliary piston rod 49 connected thereto in the manner illustrated with respect to the connection of rod 43 to the piston 45 in Fig. 2. In any event, and for the sake of illustration, let it be assumed that an accentuated upward movement of tracer spindle 26 will cause an upward movement of contactor I26. On the other hand an accentuated downward movement of spindle 26 will cause the correspondingdownward movement of contactor I26.

A micro-switch is indicated at I21 electrically operable upon upward movement of contactor I26, said switch controlling relay box I28 grounded at I28, through wires I30, whereby a current impulse fromthe source of current I3I is directed through wire I32 to solenoid coil I33 grounded at I34.

The longitudinally movable member I35 within coil I33 is adapted upon energization thereof to cause a translation to the left of the support I36 to which is pivotally joined at I 31 lever I36. Said lever pivotally mounted at I39 is adapted for pivotal movement around axis I39 whereby the outer end I40 of lever I36 may be employed as an intermittent actuating means to the right for obtaining through a suitable ratchet mechanism described hereinafter, one-quarter turns in one direction of directional control valve rotor II.

In a like manner a second micro-switch I is operable upon downward movement of contactor I26, to actuate relay box I42 grounded at I43 by means of the electrical wires I44. In turn, relay box I42 permits a current impulse from the power source I45 to travel through wire I46 to solenoid coil I41, the latter being groundedalso at I34.

On energization of coil I41 the longitudinally movable member I48 causes a translation to the left of lever support I49 to which is pivoted lever I 60 at point II. Said lever pivotally mounted at I52 thereby provides a translatory movement to the right of its outer end I53 to which may be attached suitable ratchet means for rotatably actuating with one quarter turns at a time the directional control valve rotor 11, but in the direction opposite to the direction of rotation imparted by solenoid I33.

The electrical tracer actuated mechanism above described in conjunction with Fig. is adapted for effecting quarter turns of the directional control valve rotor 11 in the manner illustrated in Figs. 17 through 19.

While Fig. 17 illustrates a hydraulic method of actuating levers I38 and I 50, as described hereafter, yet the same arrangement is perfectly adaptable to the corresponding solenoid actuated levers I36 and I60 described in conjunction with Fig. 10.

with the reciprocable supports I36 and I46 shown both in Figs. 10 and 17, it is contemplated that their reciprocable movements be eflected assaesa either electrically in the manner illustrated in conjunction with Fig. 10 or hydraulically as illustrated in Fig. 17.

It will be noted that rotational movement of rotor 11 of the directional control valve 6I was accomplished hydraulically as shown in Figs. 2, 6, 7 and 8 by means of the rack gears 8i and 66, and the idler gears 36 and 61. However Fig. 17 illustrates a hydraulic method for accomplishing this result employing levers I33 and I60 instead of gears.

Referring to Fig. 17 the lever I36 pivoted to housing I64 at I36 is joined to the reciprocable support I36 at I31 as shown also in Fig. 10. Upon downward movement oi. support I36, it is seen that upward movement is imparted to the outer end I of lever I36.

A cantilever I66 Joins lever I33 at I46 whereby downward movement of support I36 causes an upward translation of cantilever I66. Said cantilever has a ball shaped actuating means I66 at one ,end thereof with its other end joined at I51 to the coiled spring I63 anchored to housing I64 at point I 69.

Rotatable shaft II of directional control valve 6I has keyed thereon the two ratchet cam members I60 and I6I arranged in spaced relation, cam I6I being shown in Fig. 17 as having the four quadrantally disposed notches I62 intermittently and progressively engageable by the ball means I65on the end of cantilever I64 hereafter described. On the other hand the ball actuating means I56 of cantilever I66 is adapted to engage similar notched recesses I66 in the cam member I60.

A suitable guide pin I63 is carried by housing I64 adaptable for guidingly engaging the edge of cantilever I55. In operation, on downward movement of support I 36, with spring I66 maintaining cantilever I56 against pin I63, an upward movement is imparted to the ball means I56 causing the same to operatively engage the cam I60 within one of its notches I66 which correspond to notches I62 of cam I 6|.

- A 90 degree rotational movement is thus imparted to rotor 11 after which, support I36 is returned to its initial pofition, as where the solenoid coil is de-energized as described in connection with Fig. 10. On support I36 returning upwardly to its inoperative position the end I40 01' lever I36 is dropped downwardly causing the ball means I56 to disengage .cam member I60.

From the above description; an accentuated movement upwardly of the tracer spindle caused when the tracer tip engages the point I 2| in Fig. 4, will effect through solenoid I33, a translation to the left of support I36. This corresponds to a downward movement of the support I36 shown in Fig. 17. This movement thus causes thru lever I36 a ninety degree rotational movement counter-clockwise of rotor ll of the directional control valve, causing said rotor to turn from its number 3 position of Fig. 4 to its number 2 position.

Again on the tracer reaching point I22 in Fig. 4 another accentuated upward movement is eflected in the tracer spindle, which again causes another ninety degree rotation of directional control valve rotor 11 through operation of cantilever I66. Now as the tracer reaches point I24 oi templet I6 in Fig. 4, an accentuated downward movement of the tracer spindle results, causing actuation of contactor I26 against the micro-switch I4I.

This in turn causes operation of solenoid I41 causing movement to the left of support I49, and pivotal movement of lever I50 counter-clockwise. Referring to Fig. 1'1 this movement corresponds to the translation to the right of support I49 and the lever I50 joined thereto at I'5I. Said lever pivoted to housing I54 at I52 is thus given a translatory movement of its outer end I53 to the left causing a corresponding movement of cantilever I66.

Said cantilever pivotally joined to lever I50 at I53, has a ball actuating means I65 at one end, with its other end at I66 being joined to spring I61 anchored to housing I54 at I59. A corresponding cam member I6I identical with cam I66 is also keyed to shaft 11 of directional control valve 6i, having corresponding notches I62 arranged similarly to notches I660! cam I60. Thus upon translation to the right 01' support I49, a corresponding translation to the left is effected of cantilever I64 with its ball means I65 on its end operatively actuating cam I6I within one of its notches I62.

A suitable guide pin I69 is also employed secured to housing I54 providing guide means for the return of cantilever I64 at the time that solenoid I 61 is de-energized. Thus, as above described, when the tracer spindle arrives approximately at point I26 of templet 15 in Fig. 4, the accentuated downward movement of the spindle causes a 90 degree rotation clockwise of rotor 11 returning the same to its number 2 position shown.

In traversing templet 14 Fig. 3 it is seen that there will be successive accentuated downward movements of the tracer spindle at approximately points H1, H6, II9 and I20, all resulting in successive, but intermittent clockwise ninety degree adjustments of rotor 11 oi! the directional control valve to the respective numbered positions 4, I, 2 and 3 shown in Fig. 3.

Again referring to Figs. 17 through 19 specifically it is seen that the ninety degree adjustments of the directional valve rotor 11 may be eiTected hydraulically. Hydraulic cylinders I10 and "I are shown at right angles secured exterior of the housing member I54 within which ar provisioned levers I36 and I50 for rotatively actuating rotor 11 either clockwise or counterclockwise as described in detail fully relative to the operation of the electrical actuated means illustrated in Fig. 10.

Reciprocable pistons I12 and I16 and rods I14 and I15 respectively are disposed within cylinders I10 and I] I for actuating the movable lever supports I36 and I49 secured by nuts I16 and I11. High ressure fluid ports I16 and I19 are provided for fluid communication from the automatic tracer operated control valve 42 shownin Figs. 2 and 20 to the respective control cylinders I10 and HI.

As described above in connection with Fig. 2 and more particularly in Fig. 20 depending upon accentuated tracer control movements, fluid supplied to the control valve 42 through conduit 59 from hydraulic unit 51 travels out through.

either conduits 66 'or 69 to the control cylinders I10 or I15 respectively.

Such control fluid enters cylinder I 10 at Port I18, or cylinder i'II through port I19, for obtaining the initial translation of the pistons I12 or I13. its also above explained. with the control piston 65 returned to its neutral position, constant low pressure fluid is directed from the hydraulic unit 51 to the opposite ends of cylinders I10 and "I through conduit 62, causing either piston last operative to return to its neutral position. For this purpose low pressure ports I60 and I6I are provided respectively.

The exhaust fluid from cylinders I10 and "I returning through either conduit 66 or 69 isreturned back to the hydraulic unit through conduit I25 in the manner fully explained in connection with Fig. 2.

Referring again to Figs. 1"! through 19 the shaft 11 of directional control valve 6I indicated fragmentarily in Fig. 19, is manually operable through hand wheel 16. It is noted that the housing I54 for the levers I66 and I50, cantilevers I55 and I64, and cylinders I10 and "I, is suitably secured to the directional control valve housing 6| by the bolts I82 as in Fig. 19.

Fig. 19 shows the two notched cams I and I6I secured to rotatable shaft 11 with cantilever I55 shown in engagement with cam I60. From these illustrations it is seen that cantilevers I55 and I64 after their operative engagement with cams I60 and I6I respectively, are disengaged therefrom so that it appears clear that either cantilever is operable independently of the other.

It will be noted that the illustration of Fig. 20 corresponds closely to the illustration of Fig. 2 with the exception that the tracer housing I0 and control housing 42 are shown in greater detail. From the detail in Fig. 20 it is seen that spindle 26 is independent of the control piston 26 within the tracer sleeve I0.

Spindle 26 has provisioned at its upper end the Y shaped cone race I62, within which is nested the ball bearing retainer I66 for i'riction minimizing engagement with the corresponding annularly arranged bottom portion I84 0! the tracer control valve 28.

By virtue of the angular relation specified lateral pressure upon tracer tip 21 from the templet causes upward movement of the valve piston 28. Piston rods 31 and 49 however are interconnected differently than shown in Fig. 2. A fulcrum supporting member I is provisioned upon the connector plate 4I providing a base for the fulcrum I86 which is adjustably threaded upon the lever I61.

Said lever has ball ends I66 and I89 adlustab y secured by the connection members I90 and I9! threadably secured respectively upon the upper end of piston rods 31 and 49, whereby it is seen that manual adjustments may be made between said rods for regulating the corresponding movements thereof.

By varying the positioning of fulcrum I66 on lever I61 the response of the control valve 45 may be adjusted relative to the movement of the tracer controlled piston 26. This adjustment is arranged so that the nominal deflections of the tracer spindle will not appreciably eil'ect the control valve 45. While on the other hand the accentuated upward and downward movement of the spindle, on encountering certain critical changes of direction in the edge of the templet, will cause operation of the control piston 45 for regulating the rotary adjustments of directional control valve 6|, all as fully described in detail herein above.

Referring to Figs. 1 and 2 a secondary tracer 6 is shown carried by brackets 1, and the vertically adjustable slide I9 governing vertical movement of cutter l6. It is contemplated that in addition to the complete 360 degrees circumambulatory traverse effected between the tracer 21 and templet 21, and cutter I6 and work piece it, there will also be automatic tracercontrolled relative vertical feed movements of the cutter l8 relative to said work piece.

This is accomplished by the secondary tracer 6 wherein tracer spindle I92 is adapted to cooperatively engage model 9 also supported upon work table II. Said model is so formed as to correspond in profile to the vertical configuration of the pattern sought to be reproduced in the work piece.

The tracer construction is the same as that shown in Fig. but with the governor openings 32, 33 and 3B omitted. As shown diagrammatically in Fig. 2 tractor 6 is supplied fluid under pressure from the hydraulic unit 51 through conduit I94, with an exhaust conduit I95 shown for returning exhaust fluid from the vertical feed control cylinder 2.

Depending upon the vertical positioning of the spindle actuated valve within tracer 6, fluid is thus supplied under pressure to cylinder 2 through either conduit I96 or I91 to one side or the other of piston 3 therein. Thus by operation of fluid through either conduit I96 or I91 vertical movements will be effected of the cylinder 2 relative to the stationary piston rod 4 secured to the milling machine slide support 20 at point 5.

Cylinder 2 being secured to the cutter carryin slide I9, it is seen that automatic vertical adjustments oi the cutter may be effected at the same time as the relative 360 degree circumambulatory traverse is effected between cutter l8 and work piece l8. Y

It will be understood that the references here-- in to a pattern engaged by the tracer and a templet engaged by the tracer are synonomous in the present application wherein templet and pattern are intended to refer to the illustrations of Figs. 3 and 4.

Having described our invention. reference should now be had to the claims which follow for determining the scope thereof.

We claim:

1. The combination with a cutter "and work support relatively movable transversely in two directions; of a tracer engageable with a templet for controlling relative movement in one direction of said work support; a constant fluid pressure source controlling relative movement in a second direction; a safety exhaust mechanism within said tracer for limiting relative movement in said second direction; a directional control valve for regulating said relative transverse movements, and adapted to transfer tracer control from one transverse movement to the other, and change the constant fluid pressure source from one transverse movement to the other, and at the same time switching said safety mechanism from one transverse movement to the other, and means joining said tracer with said directional control valve for causing automatic adjustments of the latter.

2. The combination with a rotatable cutter, of a work support movable relatively in two directions at right angles, a plurality of cylinders with movable pistons secured to said support for reciprocably moving the same for longitudinal .and cross-feeding; of a tracer adapted to reactively engage a templet for regulating fluid under pressure to said cylinders, controlling longitudinal feed, a constant fluid pressure source for cross feeding, a safety valve in said tracer for governing the cross-feed; a directional control valve for alternately changing tracer control from longitudinal to cross-feed, and said constant feed from cross-feed to longitudinal feed, and-at the same time changing the safety control from cross-feed to longitudinal feed, and tracer operative means engageable with said directional control valve for causing automatic adjustments thereof.

3. In a hydraulic profiling and contouring duplicating mechanism, a cutter; a work support relatively and reciprocably movable in two directions by virtue of a plurality of movable pistons in hydraulic cylinders for transverse longitudinal and cross feeds of said support; a templet engaging tracer for controlling one of the transverse feeds, a constant fluid pressure source for operating the other transverse feed, a safety valve within and operated by said tracer for limiting said other transverse feed; a directional control valve for changing tracer control from one transverse feed to the other, and said constant fluid pressure source from one transverse feed to the other, and tracer controlled means operatively engaging said directional control valve for automatically adjusting the same.

4. In a hydraulic profiling and contouring duplicating mechanism, a cutter; a work support relatively and reciprocably movable in two directions by virtue of a plurality of movable pistons in hydraulic cylinders for transverse longitudinal and cross feeds thereof; a templet engaging tracer for controlling one of the transverse feeds; a constant fluid pressure source joined to the other transverse feed, a safety valve operable within said tracer for controlling said other transverse feed; a directional control valve for changing tracer control from one transverse feed to the other, changing the constant fluid source from one transverse feed to the other: and for changing safety valve control from one transverse feed to the other, said directional control valve being rotatable into positions for alternately regulating reciprocation of said transverse feeds, and tracer operative means engageable with said directional control valve for causin automatic rotational adjustments thereof.

5. In a hydraulic profiling and contouring duplicating mechanism having a cutter and a work support relatively movable in two directions at right angles, and'having a plurality of cylinders with reciprocable pistons secured to said support for actuating the same; a tracer adapted to engage a templet, a plurality of valves within said tracer and actuated thereby, for controlling fluid to one of said cylinders, and exhaust from the other, a hydraulic unit for producing fluid under pressure to said tracer, and a constant fluid source exterior of said tracer, a directional ,control valve for switching tracer control from one transverse feed movement to the other, and switching the constant pressure source from one transverse feed to the other. conduits from said hydraulic unit to said tracer, to said directional control valve, and from the latter to said cylinders, and tracer operative means engageable with said directional control valve for causing automatic adjustments thereof.

6. In a hydraulic profiling and contouring duplicating mechanism having a cutter and a plurality of cylinders for transverse longitudinal and cross feeding ofa work table relative to said cutter, and having a tracer with a control valve and a governor valve for controlling the hydraulic connections to said cylinders; a directional control valve comprising a housing having cylinder ports adaptable for fluid connection to the opposite ends of the cylinders governing transverse feeding, and inlet and return ports "adapted for rsnnection to both ends of said control valve, to a governor exhaust valve in said,

cation of said transverse feeds and also intermittently reverse tracer control from one transverse feed cylinder to the other, changing the constant fluid source from one transverse feed to the other, at the same time shifting governor valve control from one transverse feed cylinder to the other, and operative means interconnecting said tracer control valve and said directional control valve for effecting automatic adjustments of the rotatable member therein.

'1. In a hydraulic profiling and contouring duplicating mechanism having a cutter and a plurality of cylinders for transverse longitudinal and cross-feeding of a work table relative to said cutter, and having a tracer with control valve and exhaust governor valve for regulating the hydraulic connections to said cylinders; a directional control valve comprising a housing having a plurality of cylinder ports for fluid connection to the opposite ends of the transverse feed cylinders, and inlet and return ports adapted for connecting with said control .valve in said tracer, with said governor, and with a fluid pressure source; a rotatable member therein having a plurality of non-communicating channels adapted for continuous fluid communication separately at the ends thereof with each of said cylinder ports, the other ends of said channels having radial openings in said rotatable member adapted for progressive alternate communication with each of said inlet and return ports, and operative means interconnecting said tracer control valve and said directional control valve rotatable member for efiecting progressive automatic adjustments thereof.

8. In a hydraulic profiling and contouring duplicating mechanism having a cutter and a plurality of cylinders for transverse longitudinal and cross feeding of a work table relative to said cutter, and havinga tracer with control valve and exhaust governor valve for'regulating the hydraulic connections to said cylinders; a direc- I tional control valve comprising a housing having a plurality of inlet and return ports and cylinder ports, a rotatable member journaled therein with a plurality of spaced annular openings coinciding separately with each cylinder port, there being a plurality of non-communicating channels within said member, separately joining on their ends each of said annular openings, the other ends thereof having independent radial channels sepa rately joining each of said inlet and return ports, each of said cylinder ports being adapted, upon movement of said rotatable member, to progressively and alternately communicate with each of said inlet and return ports, and operative means interconnecting said control valve and said directional control valve rotatable member for effecting automatic ninety degree adjustments thereof.

9. In a hydraulic profiling and contouring duplicating mechanism having a cutter and a plurality of cylinders for transverse longitudinal and cross feeding of a work table relative to said cutter, and having a tracer with a control valve for regulating the hydraulic connections to said cylinders; a directional control valve comprising a housing having a plurality of cylinder ports and a plurality of radially spaced inlet and return ports, a manually rotatable member iournaled therein having a plurality of longitudinally spaced annular recesses separately coinciding with each cylinder port, there being a plurality of non-communicating channels of varied lengths within said member, separately joining at their ends each of said annular recesses, the other ends of said channels having independent radial channels for separately communicating with each of said inlet and return ports, each of said latter channels beingadapted upon rotation-of said member to progressively communicate separately with each of said radial inlet and return ports, and a plurality of operativemeans for causing successive and alternate ninety degree movements of said rotatable member in opposite directions.

10. The combination, a plurality of fluid cylinders for causing relative longitudinal and cross feeding movement between a cutter and a work support, a directional control valve joined by conduits to said cylinders for regulating movement thereof, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, a tracer engageable with a pattern for regulating tracer controlled fluid to said directional control valve, fluid operative means engageable with said directional control valve rotatable member for'turning the same in opposite directions, a secondary control valve communicating with said fluid operative means, and means interconnecting said tracer and said secondary control valve.

11. The combination, a plurality of fluid cylinders for causing relative longitudinal and crossfeeding movement between a cutter and a work support, a directional control valve joined by conduits to said cylinders for regulating movement thereof, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, a tracer engageable with a pattern for regulating tracer controlled fluid to said directional control valve, oppositely disposed fluid cylinders engageable with said rotatable member for turning the same inopposite directions, a secondary control valve communieating by conduits with said latter-fluid cylinders,

and operative means interconnecting said tracer and said secondary control valve.

12. The combination, a plurality of fluid cylinders for causing relative longitudinal and cross feeding movement between a cutter and a work support, a directional control valve joined by conduits to said cylinders for regulating movement thereof, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, a tracer engageable with a pattern for regulating tracer controlled fluid to said directional control valve, oppositely disposed fluid cylinders having reciprocable pistons therein engageable with said rotatablemember for turning the same in opposite directions, a secondary fluid control valve communicating by conduits with the ends of said latter fluid cylinders for causing successive and intermittent ninety degree rotation of said rotatable member in opposite directions, and operative means interconnecting said tracer and said secondary control valve.

13. Thacombination, a plurality of fluid cylinders for causing relative longitudinal and cross feeding movement between a cutter and a work support, a directional control valve joined by conduits to said cylinders for regulating movement thereof, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, a tracer engageable with a pattern for regulating tracer controlled fluid to said directional control valve, oppositely disposed fluid cylinders having reciprocable pistons therein engageable with said rotatable member for turning the same in opposite directions, a secondary fluid control valve communicating by conduits with the ends of said latter fluid cylinders 1 for causing successive and intermittent ninety degree rotation of said rotatable member in opposite directions, operative means interconnecting said tracer and said secondary control valve, and conduits communicating with the opposite ends of said latter cylinders providing a constant fluid pressure source for normally maintaining the pistons therein in inoperative position.

14 The combination, a plurality of fluid cylinders for causing relative longitudinal and cross feeding movement between a cutter and a work support, a directional control valve joined by conduits to said cylinders for regulating movement thereof, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, a tracer engageable with a pattern for regulating tracer controlled fluid to said directional control valve, operative means on said rotary member, oppositely disposed fluid cylinders having reciprocable pistons therein engageable with said operative means for turning the same in opposite directions, a secondary fluid control valve communicating by conduits with the ends of said latter fluid cylinders for causing intermittent trans lation of the pistons joining said operative means for providing ninety degree rotation of said rotatable member in either direction, operative means interconnecting said tracer and said secondary control valve, and conduits communicating with the opposite ends of said latter cylinders providing a constant fluid pressure source for normally maintaining the pistons therein in inoperative position.

15. The combination, a directional control valve housing joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, and operative means carried by said pistons adapted to independently engage said rotary member for caus ing intermittent successive one quarter turns thereof in the same direction and in opposite directions.

16. The combination, a directional control valve housing joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, operative means carried by said pistons adapted to independently engage said rotary member for causing intermittent successive one quarter turns thereof in the same direction and in opposite directions, and a secondary tracer controlled valve joined by conduits to the ends of said latter cylinders for causing translation of either of said piston carried operative means.

17. The combination, a directional control valve housing joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, operative means carried by said pistons adapted to independently engage said rotary member for causing intermittent successive one quarter turns thereof in the same direction and in opposite directions, a secondary tracer controlled valve joined by conduits to the ends of said latter cylinders for causing translation of either of said piston carried operative means, and a constant fluid pressure source joined to the opposite ends of said latter cylinders for causing return of said operative means independent of said rotary member.

18. The combination, a directional control valve housing joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, and operative means carried by said pistons adapted to independently engage said rotary member for causing upon translation thereof in one direction, intermittent successive one-quarter turns thereof in the same direction and in the opposite direction, and a constant fluid pressure source joined to the opposite ends of said latter cylinders for causing return of said operative means independently of said rotatable member.

19. The combination, a directional control valve housing Joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, rack gears carried by said pistons, idler gears carried by said rotatable member and in mesh with said rack gears respectively, and means interposed between said idler gears and said rotary member whereby upon movement of said rack gears alternately in one direction, rotational movement of said rotary member will be effected, while movement of said rack gears in the other direction, rotational movement of said rotary mem-- her will not be eflected.

20. The combination, a directional control valve housing joined by conduits to opposite ends of longitudinal and cross feed cylinders, a rotary member within said directional control valve adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely disposed fluid cylinders having reciprocable pistons therein, rack gears carried by said pistons, idler gears carried by said rotatable member and in mesh with said rack gears respectively, and means interposed between said idler gears and said rotary member whereby upon movement of said rack gears alternately in one direction, rotational movement of said rotary member will be eflected successively in one-quarter turns in one direction and in opposite directions, and a constant fluid pressure source joined to the opposite ends of said latter cylinders for causing return of said rack gears to their initial positions independent of said rotary member.

21. The combination, a directional control valve housing joined to opposite ends of longitudinal and cross feed cylinders, a rotary'member therein adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, oppositely arranged lever means adapted to operatively engage said rotary member, adaptable upon translation thereof for causing progressive one-quarter turns of said rotary member in the same direction and in opposlte directions, electrically operable means adapted for causing separate translation of said lever means, and a selective tracer controlled switch means for causing operation of either of said electrically operable means.

22. The combination, a directional control valve housing joined to opposite ends of longitudinal and cross feed cylinders, a rotary member therein adapted for directing tracer controlled fluid to one cylinder and constant pressure fluid to the other cylinder, alternately and to opposite ends thereof, separately operable ratchet means engageable with said rotary me n= ber, lever means joining said ratchet means adaptable upon translation thereof for causing progressive one-quarter turns of said rotary member in the same direction and in opposite directions, electrically operable solenoids to which said-lever means are joined for causing intermittent translation thereof, electrically operable relay means joining each of said solenoids, micro-switch means joining each of said relay means, and a tracer actuated contactor for independently engaging either of said switch means for causing rotary movements of said direction control valve rotary member.

23. The combination with a cutter and work support relatively movable transversely in two directions at right angles, a feed cylinder connected to each support to move the same a tracer engageable with a pattern for controlling one of said cylinders for relative movement in one direction; a constant fluid pressure source controlling the other cylinder for relative movement in a second direction; a directional control valve regulating said relative movements, and adapted to reverse tracer control from one cylinder to the other, and change the constant fluid pressure source from one cylinder to the other, and means joining said tracer with said directional control valve for causing automatic adiustments thereof, whereby a continuous 360 degree relative traverseis efiected between tracer and pattern, and cutter and work support.

24. The combination with a stationary rotatable cutter, of a work support movable relatively in two directions at right angles, and a plurality of cylinders with movable pistons secured to said support for reciprocably moving the same for longitudinal and cross-feeding; of a tracer adapted to engage a pattern for regulating fluid under pressure for controlling the longitudinal feed cylinder; a constant fluid pressure source for controlling the cross feed cylinder; a directional control valve for alternately changing tracer control from longitudinal to cross feed, and said constant feed from cross feed cylinder to longitudinal feed cylinder, and means joining said tracer with said directional control valve for causing automatic rotational adjustments thereof, whereby a continuous 360 degree relative traverse is eifected between tracer and pattern, and cutter and work support.

25. In a hydraulic profiling and contouring duplicating mechanism, a cutter; a work support relatively movable in two directions by virtue of a plurality of movable pistons in hydraulic cylinders for transverse longitudinal and cross feeds of said support; a pattern engaging tracer for controlling one of the feed cylinders; a constant fluid pressure source for operating the other feed cylinder; a directional control valve for changing tracer control from one feed cylinder to the other, and said constant fluid pressure source from one feed cylinder to the other, and means joining said tracer with said directional control valve for causing automatic adjustments thereof whereby a continuous 360 degree relative traverse is efiected between tracer and pattern, and cutter and work support.

26. In a hydrauli profiling and contouring duplicating mechanism, a cutter; a work support relatively and reciprocably movable in two directions by virtue of a plurality of movable pistons in hydraulic cylinders for traverse longitudinal and cross feeds of said support; a pattern engaging tracer for controlling one of the feed cylinders; a constant fluid pressure. source joined to the other feed cylinder; a directional control valve for changing tracer control from one feed cylinder to the other, and changing the constant fluid source from one feed cylinder to the other, said directional control valve being movable into position for alternately regulating reciprocation of said transverse feed cylinders, and means joining said tracer with said directional control valve for causing automatic adjustments thereof whereby a continuous 360 degree relative traverse is efiected between tracer and pattern, and cutter and work piece.

27. In a. hydraulic profiling and contouring duplicating mechanism having a cutter and a work support relatively movable in two directions at right angles with respect to eacn other, and having a plurality of cylinders with reciprocable pistons secured to said support for actuating the same; a tracer adapted to engage a pattern, a valve therein for controlling fluid selectively to either of the two cylinders, a second valve for controlling the exhaust fluid from the cylinder not under tracer control, a hydraulic unit for providing fluid under, pressure to the feed cylinder controlling valve in said tracer, and also a constant fluid source exterior to said tracer for the feed cylinder not under tracer control, a directional control valve mechanism for switching tracer control from one transverse feed cylinder to the other, and switching the constant pressure source from one transverse feed to the other respectively, suitable conduits from said hydraulic unit to said tracer to said directional control valve and said cylinders, and means joining said tracer with said directional 

